US2139050A

US2139050A - Viscosity compensating device

Info

Publication number: US2139050A
Application number: US140073A
Authority: US
Inventors: Harry F Vickers
Original assignee: Individual
Current assignee: Individual
Priority date: 1937-05-01
Filing date: 1937-05-01
Publication date: 1938-12-06
Anticipated expiration: 1955-12-06

Description

Dec. 6, 1938. H. F. VICKERS VISCOSITY COMPENSATING DEVIGE File d May 1, '19s? 2 Sheets-Sheet 2 Fm mm 1 may INVENTOR. HERE! F V/CKERJ BY M W W WM ATTORNEY$ Patented Dec. 6, 1938 UNITED STATES PATENT OFFICE VISCOSITY COMPENSATING DEVICE HarryF. Vickers, Detroit, Mich.

Application May 1, 1937, Serial No. 140,073

9 Claims.

pensating device and has particularly to do with a flow control valve which is provided with a means to compensate for change in viscosity of the oil or pressure fluid in a pressure work system.

It is well known that in the use of machine tools, the rate of movement of the table member, or the ieedmember bearing the cutting tool.

must,; as a rule, be very constant. In adapting hydraulically'actuated devices tomachine shop use, the greatest problem has been to achieve accurate and constant ieed rates under varying conditions of load. One of the contributing factors to inaccuracy has been the change in the viscosity of the liquid used in the hydraulic sys-- tem, due to changes in temperature. Various speed control valves have been devised-to control the flow oi-pressu'reliquid to or from the liquid actuated devices, but none of them have attempted to provide compensating means for changes in viscosity of'the pressur'e' liquid. Y 1

-The present invention contemplates theuse of acompensating means on: a flow or speed control means similar to that disclosed in my copending application Serial No. 543,908; said compensating means being arranged to automatically adjust the flow control mens for changes in viscosity of pressure oil due to changes in temperature; r

My speedor fiow control devicehas an orifice regulatabie to control the fiow "of liquid therethrough, andis especially adapted to regulate the speed of a liquid-actuated element hydraulically connected to said flow control means. The device embodies a hydrostatic pressure regulating valve; preferably in combination as a simple unit with a variable orifice, said hydrostatically operated valve being so arranged and proportioned in load, nor a change in viscosity due to a temperature change of the liquid will increase or decrease the fiow across the orifice and thereby maintain constant the speed of the liquid actuated element.

As contemplated by the present invention the movement of this hydrostatic pressure regulating valve, which normally maintains a constant pressure differential across the outlet orifice, is to be partially controlled by a spring, the tension oi. which will be varied directly, with the temperature of the oil in the system. The device is so arranged that an increase or decrease in the viscosity of the oil due to temperature changes, 65 which changes the flowing properties of the oil,

that neither a change in pressure due to a change This invention relates to a viscosity com-- will be compensated for by a reduction in the opening pressure of the hydrostatic valve.

The invention is especially adapted for use in a hydraulic system containing either a constant or a variable volume pump. In practice, in systems using variable pumps fairly good results are often obtained when the work is first set up, but when the oil warms up and thins, and as the tools become dull, there is a noticeable slowing up due to a change in the slippage in the variable pump. r

In the drawings:

Fig. 1 shows a modification of the invention as embodied in a fiow control valve and used with 'a cylinder motor.

Fig. 2 is a plotting of' the mercury correction curve of the modification shown in Fig. 1 with the viscosity curve of the oil.

Fig. 3 is similar to Fig. 1 showing a modified structure for the compensating means.

Fig. 4 is a plotting of the correction curve of the modification shown in Fig. 3.

Referring to Fig. l a pressure conduit 5 leads to one end of a cylinder motor 6 in which operates a piston I. From the other end of the cylinder motor 6 is a'conduit 8 leading to a housing of the vflow control valve generally designated 9. The housing 9 is provided with achamber I0 7 in' communication with'the incoming liquid conpiston l6 by means of a passageway l9, while the conduit M, on the other side of the outlet valve I3, is in communication with the chamber l8a on the other side of the piston Hi by means of a. passageway l9a. The variable orifice outlet valve l3 may be adjusted from theoutside of the valve housing 9 by a lever 20. In a housing 90. which is directly adjacent the housing 9, are 10- cated spring. 2i, a plunger 22 and a spring 23, all of which back the piston IS. The spring 23 is considerably stronger than the spring 2|. The plunger 22 operates in a chamber 24 which is connected by a passage 25 to a chamber 26. In the chamber 26 is a body of mercury or other fluid substance which expands when heated.

In the operation: As explained in my copending application previously referred to, the balanced valve I2 is provided with the piston l6 which is exposed on each side to the respective pressures on each side of the orifice of the outlet or flow control valve l3. This balanced valve serves to maintain a constant differential pressure across said orifice, said difi'erential being determined by the spring 2| acting on said piston i6. If the compression of the spring is lessened the differential will be decreased.

Referring now to the function of the present invention, it will be seen that the plunger 22 has an area exposedto the mercury in chamber 26. The temperature of the mercury is controlled by conduction of heat through the body of the valve, and an increase in temperature will cause expansion of the mercury which will in turn move the plunger 22 to the right thereby compressing spring 23 and lessening the compression of the spring 2i. The result will be that the pressure differential across the valve l3 will be decreased. This reduction in pressure differential will compensate for the fact that oil at increased temperature would normally flow more rapidly through the orifice in the outlet valve l3.

In Fig. 2 it will be noted that the temperature of the viscosity curve designated oil, is approximately a logarithmic curve. The movement of the plunger 22 caused by the mercury expansion may be plotted as a straight line in comparison to the temperature. The mercury pressure correction line, therefore, will be a straight line approximately following the viscosity curve through the normal temperature range.

The modification shown in Fig. 3 has the same general valve structure as that shown in Fig. 1. In this modification, however, the valve piston i 6 is backed by a single spring 21.

At the left end of the valve housing 9 is a housing 28 provided with a mercury chamber 29 into which projects a rod 30 which is directly connected to a plunger 3|, the latter having a cam surface 32. A slidable plunger spring seat 33 has a bullet shaped nose 34 which contacts the cam surface 32. This spring seat 33 contains a spring 35 which bears on the end of the balanced inlet valve l2 to counteract the action of the spring 21. The compression of the spring 35 is directly controlled by the position of the plunger 3 I. The expansion of the mercury in the chamber 29 will act on the rod 30 which projects into said mercury and will tend to move the rod upwardly thereby changing the position of the plunger 3| and compressing the spring 35. It will be seen that the higher the temperature of the pressure liquid, the greater will be the expansion of the mercury and the movement of the plunger 3|. The compression of the spring 35, therefore, will have a definite relationship to the temperature of the pressure liquid. The springs 21 and 35 are, of course, originally adjusted to maintain a predetermined pressure difl'erential across the orifice of the valve l3. Any increase in the compression of spring 35 will further counteract spring 21 and decrease the resultant spring force on the orifice valve l2 thereby decreasing the aforesaid pressure differential. The device is therefore designed so that a decrease in oil viscosity will be accompanied by a suitable lowering of the pressure differential across valve l3 so that the total oil fiow through said valve l3 will always be constant. This means that the exhaust fiow from the cylinders 6 as shown in Figs. 1 and 3 may be maintained at a constant rate regardless of the viscosity changes in the pressure fiuid.

B3! plotting the logarithmic viscosity curve of the 011 against the face of the cam surface 32, it is possible to illustrate the correction for the changes in oil viscosity due to temperature. As shown in Fig. 4 the mercury pressure correction line of the last described embodiment is practically identical with the viscosity temperature curve of the oil.

What I claim is:

1. In a hydraulic constant flow control valve, an adjustable throttle orifice, a pressure balanced orifice valve to maintain a predetermined pressure differential across said throttle orifice, a mercury filled expansion chamber, means responsive to the expansion of the mercury in said chamber, and spring means operatively connecting said balanced orifice valve with said first named means to regulate said pressure differential to maintain a predetermined relationship between the pressure differential and the temperature of the flow control valve.

2. In a hydraulic constant fiow control valve, a housing, a throttle orifice formed in said housing, a pressure balanced orifice valve, spring means acting on said orifice valve to maintain a predetermined pressure differential across said throttle orifice, and temperature responsive means comprising a liquid expansion chamber formed in said housing, and a piston exposed on one side to said liquid and adapted to control the force of said spring means to alter the pressure differential across said throttle orifice thereby to allow a constant liquid flow through said valve by maintaining a predetermined relationship between the pressure differential and the temperature of the liquid fiowing through the control valve.

3. In a hydraulic liquid control valve, an adjustable throttle orifice, a pressure balanced orifice valve, spring means exerting force on said orifice valve to maintain a predetermined pressure differential across said throttle orifice, a mercury filled expansion chamber, piston means responsive to the expansion of the mercury in said chamber and operatively connected to the spring means to alter the force thereof, said spring means and piston being adapted to control the pressure differential across said throttle orifice to maintain a predetermined relationship between the pressure differential and the temperature of the liquid flowing through the control valve and thereby acting to maintain a constant liquid flow through said control valve.

4. In a hydraulic constant fiow control valve of the type having an adjustable throttle orifice, and a pressure balanced orifice valve adapted to maintain a predetermined pressure differential across said throttle orifice, a mercury filled expansion chamber, means responsive to the expansion of the mercury in said chamber, and spring means operatlvely connecting said balanced orifice valve with said first named means to regulate said pressure differential to maintain a predetermined relationship between the pressure differential and the temperature of liquid flowing through the control valve.

5. In a hydraulic constant fiow control valve, a housing, a throttle orifice formed in said housing, a pressure balanced orifice valve located in said housing to maintain a predetermined pressure differential across said throttle orifice, a liquid filled expansion chamber formed in said housing, means responsive to the expansion of the liquid in said chamber, and means mechanically and resiliently connecting said balanced orifice valve with said first named means to regulate said pressure differential to maintain a predetermined relationship between the pressure differential and the temperature of liquid flowing through the flow control valve.

6. In a hydraulic constant flow control valve, an adjustable throttle orifice, a pressure balanced orifice valve, spring means acting on said orifice valve to maintain a predetermined pressure differential across said throttle orifice, a mercury filled expansion chamber, a slidable plunger member exposed on one side to, and responsive to the expansion of, the mercury in said chamber, and spring means operatively connecting said balanced orifice valve with said plunger member to alter the effect of said first named spring means and thereby to regulate said pressure diiferential to maintain a predetermined relationship between the pressure differential and the temperature of liquid flowing through the control valve.

7. In a hydraulic constant flow control valve,

a valve housing, an outlet orifice, a pressure balanced orifice valve, spring means acting on said valve and adapted to maintain a predetermined pressure differential across said throttle orifice, a fluid expansion chamber in said valve housing containing a fluid which expands with increased temperature, a piston means exposed on one side to said expansion chamber, and spring means mechanically connecting said piston means with said orifice valve to alter the effect of said first named spring means whereby to regulate said differential pressure, said orifice valve, expansion chamber, piston means, said second named spring means cooperating to maintain aidefinite predetermined relationship between said pressure dif-- ferential and the temperature of liquid flowing through said valve housing.

8. In a hydraulic system having a viscous pressure fluid subject to viscosity changes with variations in temperature, a constant flow control valve comprising a valve housing, an outlet orifice, a pressure balanced orifice valve adapted to maintain a normal predetermined pressure differential across said throttle orifice, a fluid expansion chamber in said valve housing, containing a fluid which expands and contracts with temperature variations, a piston means exposed on one side to the fluid in said expansion chamber, plunger means responsive to the movement of said piston means, and a spring operatively connecting said plunger to said orifice valve to regulate said differential pressure.

9. In a hydraulic system having a viscous pressure fluid subject to viscosity changes with variations in temperature, a constant flow control .valve comprising a valve housing, an outlet oriflce, a pressure balanced orifice valve adapted to maintain a normal predetermined pressure dif-- ferential across said throttle orifice, a fluid expansion chamber in said valve housing containing a fluid which expands and contracts with temperature variations, a piston means exposed on one side to the fluid in said expansion chamber, cam means responsive to movement of said piston having a cam surface identical to the curve obtained by plotting the logarithmic viscosity curve of said pressure fluid, said cam means being operatively connected to said orifice valve to regulate said difierential pressure in relation to temperature variations such that differential pressure will decrease at a predetermined rate relative to temperature increase and viscosity decrease of the pressure fluid to maintain a constant flow of pressure fluid through said outlet orifice.

HARRY F. VICKERS.